Family of five-speed transmission mechanisms having three planetary gear sets

ABSTRACT

The family of transmissions has a plurality of members that can be utilized in powertrains to provide at least five forward speed ratios and one reverse speed ratio. The transmission family members include three planetary gear sets, two brakes and two clutches. The powertrain includes an engine and torque converter that is continuously connected to at least one member of the planetary gear arrangement and an output member that is continuously connected with another of the planetary gear members. The two brakes and two clutches provide interconnections between various gear members and with the input, the output shaft, or the transmission housing, in some instances, and are operated in combinations of two to establish at least five forward speed ratios and a reverse speed ratio.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a family of power transmissions havingthree planetary gear sets that are controlled by two clutches and twobrakes to provide at least five forward speed ratios and one reversespeed ratio.

2. Background Art

Passenger vehicles include a powertrain that is comprised of an engine,multi-speed transmission, and a differential or final drive. Themulti-speed transmission increases the overall operating range of thevehicle by permitting the engine to operate through its torque range anumber of times. The number of forward speed ratios that are availablein the transmission determines the number of times the engine torquerange is repeated. Early automatic transmissions had two speed ranges.This severely limited the overall speed range of the vehicle andtherefore required a relatively large engine that could produce a widespeed and torque range. This resulted in the engine operating at aspecific fuel consumption point during cruising, other than the mostefficient point. Therefore, manually-shifted (countershafttransmissions) were the most popular.

With the advent of three- and four-speed automatic transmissions, theautomatic shifting (planetary gear) transmission increased in popularitywith the motoring public. These transmissions improved the operatingperformance and fuel economy of the vehicle. The increased number ofspeed ratios reduces the step size between ratios and therefore improvesthe shift quality of the transmission by making the ratio interchangessubstantially imperceptible to the operator under normal vehicleacceleration.

It has been suggested that the number of forward speed ratios beincreased to five and even six speeds. Five-speed transmissions aredisclosed in U.S. Pat. Nos. 5,879,264; 5,984,825; 5,997,429; 6,007,450;and 6,056,665 issued to Raghavan, Hebbale and Usoro on Mar. 9, 1999;Nov. 16, 1999; Dec. 7, 1999; Dec. 28, 1999 and May 2, 2000,respectively; and U.S. Pat. No. 5,951,432 issued to Wehking, Hebbale,Raghavan and Usoro on Sep. 14, 1999. Six-speed transmissions aredisclosed in U.S. Pat. No. 4,070,927 issued to Polak on Jan. 31, 1978;U.S. Pat. No. 6,071,208 issued to Koivunen on Jun. 6, 2000; U.S. Pat.No. 5,106,352 issued to Lepelletier on Apr. 21, 1992; and U.S. Pat. No.5,599,251 issued to Beim and McCarrick on Feb. 4, 1997.

Five-speed transmissions offer several advantages over four speedtransmissions, including improved vehicle acceleration and improved fueleconomy. While many trucks employ power transmissions, such as Polak,having six or more forward gear ratios, passenger cars are stillmanufactured with three- and four-speed automatic transmissions andrelatively few five or six-speed devices due to the size and complexityof these transmissions. The Raghavan, Hebbale, Usoro and Wehking patentsemploy two planetary gear sets, and five or six torque transmittingmechanisms to provide five forward speeds.

SUMMARY OF THE INVENTION

It is an object of the present invention to provide an improved familyof transmissions having three planetary gear sets controlled to provideat least five forward speed ratios.

In one aspect of the present invention, the family of transmissions hasthree planetary gear sets, each of which includes a first, second andthird member, which members may comprise a sun gear, a ring gear, or aplanet carrier assembly member.

In another aspect of the present invention, each of the planetary gearsets may be of the single pinion-type or of the double pinion-type.

In yet another aspect of the present invention, a first interconnectingmember continuously interconnects the first member of the firstplanetary gear set with the first member of the second planetary gearset.

In still another aspect of the invention, a second interconnectingmember continuously interconnects the second member of the firstplanetary gear set with the first member of the third planetary gearset.

In another aspect of the invention, a third interconnecting membercontinuously interconnects the second member of the second planetarygear set with the second member of the third planetary gear set.

In yet a further aspect of the invention, each family memberincorporates an input shaft which is continuously interconnected with amember of the first, second or third planetary gear set, and an outputshaft which is continuously connected with another member of the first,second or third planetary gear set.

In another aspect of the invention, a first brake selectivelyinterconnects a member of the first, second or third planetary gear set,or one of the first, second and third interconnecting members with thetransmission housing.

In still a further aspect of the invention, a second brake selectivelyinterconnects a member of the first or third planetary gear set with atransmission housing.

In a still further aspect of the invention, a first clutch selectivelyinterconnects a member of the first or second planetary gear set or oneof the first, second and third interconnecting members with the inputshaft, the output shaft, or another member of the first, second or thirdplanetary gear set.

In a still further aspect of the invention, a second clutch selectivelyinterconnects a member of the first, second, or third planetary gear setwith another member of the first, second, or third planetary gear set.

In still another aspect of the invention, the two brakes and twoclutches are selectively engageable in combinations of two to yield atleast five forward speed ratios and one reverse speed ratio.

The above objects and other objects, features, and advantages of thepresent invention are readily apparent from the following detaileddescription of the best modes for carrying out the invention when takenin connection with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1a is a schematic representation of a powertrain including aplanetary transmission incorporating a family member of the presentinvention;

FIG. 1b is a truth table and chart of some of the operatingcharacteristics of the powertrain shown in FIG. 1a;

FIG. 2a is a schematic representation of a powertrain having a planetarytransmission incorporating another family member of the presentinvention;

FIG. 2b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 2a;

FIG. 3a is a schematic representation of a powertrain having a planetarytransmission incorporating another family member of the presentinvention;

FIG. 3b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 3a;

FIG. 4a is a schematic representation of a powertrain having a planetarytransmission incorporating another family member of the presentinvention;

FIG. 4b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 4a;

FIG. 5a is a schematic representation of a powertrain having a planetarytransmission incorporating another family member of the presentinvention;

FIG. 5b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 5a;

FIG. 6a is a schematic representation of a powertrain having a planetarytransmission incorporating another family member of the presentinvention;

FIG. 6b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 6a;

FIG. 7a is a schematic representation of a powertrain having a planetarytransmission incorporating another family member of the presentinvention;

FIG. 7b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 7a;

FIG. 8a is a schematic representation of a powertrain having a planetarytransmission incorporating another family member of the presentinvention;

FIG. 8b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 8a;

FIG. 9a is a schematic representation of a powertrain having a planetarytransmission incorporating another family member of the presentinvention;

FIG. 9b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 9a;

FIG. 10a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 10b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 10a;

FIG. 11a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 11b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 11a;

FIG. 12a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 12b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 12a;

FIG. 13a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 13b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 13a;

FIG. 14a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 14b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 14a;

FIG. 15a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

FIG. 15b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 15a;

FIG. 16a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention; and

FIG. 16b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 16a.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Referring to the drawings, wherein like characters represent the same orcorresponding parts throughout the several views, there is shown in FIG.1a a powertrain 10 having a conventional engine and torque converter 12,a planetary transmission 14, and a conventional final drive mechanism16.

The planetary transmission 14 includes an input shaft 17 continuouslyconnected with the engine and torque converter 12, a planetary geararrangement 18, and an output shaft 19 continuously connected with thefinal drive mechanism 16. The planetary gear arrangement 18 includesthree planetary gear sets 20, 30 and 40.

The planetary gear set 20 includes a sun gear member 22, a ring gearmember 24, and a planet carrier assembly 26. The planet carrier assembly26 includes a plurality of pinion gears 27 rotatably mounted on acarrier member 29 and disposed in meshing relationship with both the sungear member 22 and the ring gear member 24.

The planetary gear set 30 includes a sun gear member 32, a ring gearmember 34, and a planet carrier assembly member 36. The planet carrierassembly member 36 includes a plurality of pinion gears 37 rotatablymounted on a carrier member 39 and disposed in meshing relationship withboth the sun gear member 32 and the ring gear member 34.

The planetary gear set 40 includes a sun gear member 42, a ring gearmember 44, and a planet carrier assembly member 46. The planet carrierassembly member 46 includes a plurality of pinion gears 47 rotatablymounted on a carrier member 49 and disposed in meshing relationship withboth the sun gear member 42 and the ring gear member 44.

The planetary gear arrangement 18 also includes four torque transmittingmechanisms 50, 52, 54 and 56. The torque-transmitting mechanisms 50 and52 are stationary-type torque-transmitting mechanisms, commonly termedbrakes or reaction clutches. The torque transmitting mechanisms 54 and56 are of the rotating type torque transmitting mechanisms, commonlytermed clutches.

The input shaft 17 is continuously connected with the ring gear member24, and the output shaft 19 is continuously connected with the ring gearmember 34. A first interconnecting member 70 continuously interconnectsthe planet carrier assembly member 26 with the ring gear member 34. Asecond interconnecting member 72 continuously interconnects the sun gearmember 22 with the sun gear member 42. A third interconnecting member 74continuously connects the sun gear member 32 with the planet carrierassembly member 46.

The planet carrier assembly member 36 is selectively connectable withthe transmission housing 60 through the brake 50. The ring gear member44 is selectively connectable with the transmission housing 60 throughthe brake 52. The ring gear member 24 is selectively connectable withthe planet carrier assembly member 46 through the clutch 54. The planetcarrier assembly member 46 is selectively connectable with the ring gearmember 44 through the clutch 56.

As shown in FIG. 1b, and in particular the truth table disclosedtherein, the torque-transmitting mechanisms are selectively engaged incombinations of two to provide five forward speed ratios and one reversespeed ratio. It should also be noted in the truth table that thetorque-transmitting mechanism 50 remains engaged through a neutralcondition, thereby simplifying the forward/reverse interchange.

To establish the reverse speed ratio, the brake 50 and clutch 54 areengaged. The engagement of the brake 50 secures the planet carrierassembly member 36 to the transmission housing 60, and the clutch 54secures the planet carrier assembly member 46 to the ring gear member24. The planet carrier assembly member 26 and the ring gear member 34rotate at the same speed as the output shaft. The planet carrierassembly member 36 does not rotate. The sun gear member 32 rotates atthe same speed as the planet carrier assembly member 46, the ring gearmember 24, and the input shaft 17. The speed of the ring gear member 34,and therefore the output shaft speed, is determined by the speed of thesun gear member 32 and the ring gear/sun gear tooth ratio of theplanetary gear set 30. The overall numerical value of the reverse speedratio is determined by the ring gear/sun gear tooth ratio of theplanetary gear set 30.

The first forward speed ratio is established with the engagement of thebrakes 50 and 52. With the brake 50 engaged, the planet carrier assemblymember 36 is fixed to the transmission housing 60. The brake 52 connectsthe ring gear member 44 to the transmission housing 60. The planetcarrier assembly member 26 and ring gear member 34 rotate at the samespeed as the output shaft. This speed is determined by the speed of thering gear member 24, which is the same as the input shaft speed, thespeed of the sun gear member 22, and the ring gear/sun gear tooth ratioof the planetary gear set 20. The sun gear member 32 rotates at the samespeed as planet carrier assembly member 46. The planet carrier assemblymember 36 does not rotate. The speed of the ring gear member 34 isdetermined by the speed of the sun gear member 32 and the ring gear/sungear tooth ratio of the planetary gear set 30. The sun gear member 42rotates as the same speed as the sun gear member 22. The ring gearmember 44 does not rotate. The planet carrier assembly member 46 rotatesat a speed determined by the speed of the sun gear member 42 and thering gear/sun gear tooth ratio of the planetary gear set 40. The overallnumerical value of the first forward speed ratio is determined by thetooth ratios of the planetary sets 20, 30 and 40.

The second forward speed ratio is established with the engagement of thebrake 50 and the clutch 56. The brake 50 connects the planet carrierassembly member 36 to the transmission housing 60, and the clutch 56connects the planet carrier assembly member 46 to the ring gear member44. The planet carrier assembly member 26 rotates at the same speed asthe ring gear member 34 and the output shaft 19. This speed isdetermined by the speed of the ring gear member 24, which is the same asthe input shaft speed, the speed of the sun gear member 22, and the ringgear/sun gear tooth ratio of the planetary gear set 20. The planetcarrier assembly member 36 does not rotate. The planet carrier assemblymember 46 rotates at the same speed as the sun gear member 32 and thering gear member 44. The sun gear member 42 rotates at the same speed asthe sun gear member 22, the ring gear member 44, and the planet carrierassembly member 46. The overall numerical value of the second forwardspeed ratio is determined by the ring gear/sun gear tooth ratios of theplanetary gear sets 20 and 30.

The third forward speed ratio is established with the engagement of thebrake 52 and the clutch 56. The brake 52 connects the ring gear member44 to the transmission housing 60, and the clutch 56 connects the planetcarrier assembly member 46 to the ring gear member 44. In thisconnection, the planetary gear set 40 stays stationary. The ring gearmember 24 rotates at the same speed as the input shaft 17, and theplanet carrier assembly member 26 rotates at the same speed as theoutput shaft and the ring gear member 34. The sun gear member 22 isconnected to the sun gear member 42 and does not rotate. The speed ofthe planet carrier assembly member 26, and therefore the output shaftspeed, is determined by the speed of the ring gear member 24, the speedof the sun gear member 22, and the ring gear/sun gear tooth ratio of theplanetary gear set 20. The overall numerical value of the third forwardspeed ratio is determined by the tooth ratio of the planetary gear set20.

The fourth forward speed ratio is established with the engagement of theclutches 54 and 56. The clutch 54 connects the planet carrier assemblymember 46 with the ring gear member 24, and the clutch 56 connects theplanet carrier assembly member 46 with the ring gear member 44. In thisconfiguration, the input shaft 17 is directly connected to the outputshaft 19. The numerical value of the fourth forward speed ratio is 1.

The fifth forward speed ratio is established with the engagement of thebrake 52 and the clutch 54. The brake 52 connects the ring gear member44 to the transmission housing 60, and the clutch 54 connects the planetcarrier assembly member 46 to the ring gear member 24. The ring gearmember 24 rotates at the same speed as the input shaft 17, the planetcarrier assembly member 46, and the sun gear member 32; the sun gearmember 22 rotates at the same speed as the sun gear member 42; and theplanet carrier assembly member 26 rotates at the same speed as theoutput shaft. The speed of the planet carrier assembly 26 can bedetermined from the speed of the ring gear member 24, the speed of thesun gear member 22, and the ring gear/sun gear tooth ratio of theplanetary gear set 20. The ring gear member 44 does not rotate. Theplanet carrier assembly member 46 rotates at a speed determined by thespeed of the sun gear member 42 and the ring gear/sun gear tooth ratioof the planetary gear set 40. The overall numerical value of the fifthforward speed ratio is determined by the tooth ratios of the planetarygear sets 20 and 40.

As set forth above, the engagement schedules for the torque-transmittingmechanisms are shown in the truth table of FIG. 1b. This truth tablealso provides an example of speed ratios that are available utilizingthe ring gear/sun gear tooth ratios given by way of example in FIG. 1b.The R1/S1 value is the tooth ratio of the planetary gear set 20; theR2/S2 value is the tooth ratio of the planetary gear set 30; and theR3/S3 value is the tooth ratio of the planetary gear set 40. Also, thechart of FIG. 1b describes the ratio steps that are attained utilizingthe sample of tooth ratios given. For example, the step ratio betweenthe first and second forward ratios is 1.73, while the step ratiobetween the reverse and first forward ratio is −0.63. It can also bereadily determined from the truth table of FIG. 1b that all of thesingle step forward ratio interchanges are of the single transitionvariety, as are the double step forward ratio interchanges.

FIG. 2a shows a powertrain 110 having a conventional engine and torqueconverter 12, a planetary transmission 114, and a conventional finaldrive mechanism 16.

The planetary transmission 114 includes an input shaft 17 continuouslyconnected with the engine and torque converter 12, a planetary geararrangement 118, and an output shaft 19 continuously connected with thefinal drive mechanism 16. The planetary gear arrangement 118 includesthree planetary gear sets 120, 130 and 140.

The planetary gear set 120 includes a sun gear member 122, a ring gearmember 124, and a planet carrier assembly 126. The planet carrierassembly 126 includes a plurality of pinion gears 127 rotatably mountedon a carrier member 129 and disposed in meshing relationship with boththe sun gear member 122 and the ring gear member 124.

The planetary gear set 130 includes a sun gear member 132, a ring gearmember 134, and a planet carrier assembly member 136. The planet carrierassembly member 136 includes a plurality of pinion gears 137 rotatablymounted on a carrier member 139 and disposed in meshing relationshipwith both the sun gear member 132 and the ring gear member 134.

The planetary gear set 140 includes a sun gear member 142, a ring gearmember 144, and a planet carrier assembly member 146. The planet carrierassembly member 146 includes a plurality of pinion gears 147 rotatablymounted on a carrier member 149 and disposed in meshing relationshipwith both the sun gear member 142 and the ring gear member 144.

The planetary gear arrangement 118 also includes four torquetransmitting mechanisms 150, 152, 154 and 156. The torque-transmittingmechanisms 150 and 152 are stationary-type torque-transmissionmechanisms, commonly termed brakes or reaction clutches. The torquetransmitting mechanisms 154 and 156 are of the rotating type torquetransmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member122, and the output shaft 19 is continuously connected with the planetcarrier assembly member 136. The planet carrier assembly member 126 iscontinuously connected with the ring gear member 134 through theinterconnecting member 170. The ring gear member 124 is continuouslyconnected with the planet carrier assembly member 146 through theinterconnecting member 172. The sun gear member 132 is continuouslyconnected with the sun gear member 142 through the interconnectingmember 174.

The sun gear member 142 is selectively connectable with the transmissionhousing 160 through the brake 150. The ring gear member 144 isselectively connectable with the transmission housing 160 through thebrake 152. The sun gear member 122 is selectively connectable with theplanet carrier assembly member 126 through the clutch 154. The planetcarrier assembly member 126 is selectively connectable with the ringgear member 144 through the clutch 156.

The truth table of FIG. 2b describes the engagement sequence utilized toprovide five forward speed ratios and a reverse speed ratio in theplanetary gear arrangement 118 shown in FIG. 2a.

To establish the reverse speed ratio, the brake 152 and clutch 156 areengaged. The brake 152 connects the ring gear member 144 to thetransmission housing 160, and the clutch 156 connects the planet carrierassembly member 126 to the ring gear member 144. The ring gear member124 rotates at the same speed as the planet carrier assembly member 146.The sun gear member 122 rotates at the same speed as the input shaft 17.The planet carrier assembly member 126 and ring gear members 134, 144 donot rotate. The ring gear member 124 rotates at a speed determined bythe speed of the sun gear member 122 and the ring gear/sun gear membertooth ratio of the planetary gear set 120. The sun gear member 132rotates at the same speed as the sun gear member 142. The planet carrierassembly member 136 rotates at the same speed as the output shaft 19.The speed of the planet carrier assembly member 136 is determined by thespeed of the sun gear member 132 and the ring gear/sun gear tooth ratioof the planetary gear set 130. The planet carrier assembly member 146rotates at a speed determined by the speed of the sun gear member 142and the ring gear/sun gear tooth ratio of the planetary gear set 140.The overall numerical value of the reverse speed ratio is determinedfrom the tooth ratios of the planetary gear sets 120, 130 and 140.

The first forward speed ratio is established with the engagement of thebrakes 150 and 152. The brake 150 connects the sun gear member 142 tothe transmission housing 160, and the brake 152 connects the ring gearmember 144 to the transmission housing 160. The ring gear member 124,sun gear member 132, and planetary gear set 140 do not rotate. The sungear member 122 rotates at the same speed as the input shaft 17. Theplanet carrier assembly member 126 rotates at the same speed as the ringgear member 134. The planet carrier assembly member 126 rotates at aspeed determined by the speed of the sun gear member 122 and the ringgear/sun gear tooth ratio of the planetary gear set 120. The planetcarrier assembly member 136 rotates at the same speed as the outputshaft 19. The speed of the planet carrier assembly member 136 isdetermined from the speed of the ring gear member 134 and the ringgear/sun tooth ratio of the planetary gear set 140. The overallnumerical value of the first forward speed ratio is determined by thetooth ratios of the planetary sets 120 and 130.

The second forward speed ratio is established with the engagement of thebrake 150 and the clutch 156. The brake 150 connects the sun gear member142 to the transmission housing 160, and the clutch 156 connects theplanet carrier assembly member 126 to the ring gear member 144. The ringgear member 124 rotates at the same speed as the planet carrier assemblymember 146. The sun gear member 122 rotates at the same speed as theinput shaft 17. The planet carrier assembly member 126 rotates at thesame speed as the ring gear members 134 and 144. The speed of the planetcarrier assembly member 126 is determined from the speed of the ringgear member 124, the speed of the sun gear member 122, and the ringgear/sun tooth ratio of the planetary gear set 120. The sun gear members132 and 142 do not rotate. The planet carrier assembly member 136rotates at the same speed as the output shaft 19. The speed of theplanet carrier assembly member 136 is determined from the speed of thering gear member 134 and the ring gear/sun gear tooth ratio of theplanetary gear set 130. The speed of the planet carrier assembly member146 is determined from the speed of the ring gear member 144 and thering gear/sun gear tooth ratio of the planetary gear set 140. Theoverall numerical value of the second forward speed ratio is determinedby the tooth ratios of the planetary sets 120, 130 and 140.

To establish the third forward speed ratio, the brake 150 and clutch 154are engaged. The brake 150 connects the sun gear member 142 to thetransmission housing 160, and the clutch 154 connects the sun gearmember 122 to the planet carrier assembly member 126. The planet carrierassembly members 126 and 146 rotate at the same speed as the sun gearmember 122, the input shaft 17, and the ring gear members 124 and 134.The sun gear member 132 does not rotate. The planet carrier assemblymember 136 rotates at the same speed as the output shaft 19. The speedof the planet carrier assembly member 136 is determined from the speedof the ring gear member 134 and the ring gear/sun gear tooth ratio ofthe planetary gear set 130. The overall numerical value of the thirdforward speed ratio is determined from the tooth ratio of the planetaryset 130.

The fourth forward speed ratio is established with the engagement of theclutches 154 and 156. In this configuration, the input shaft 17 isdirectly connected with the output shaft 19. The overall numerical valueof the fourth forward speed ratio is 1.

The fifth forward speed ratio is established with the engagement of thebrake 152 and the clutch 154. The brake 152 connects the ring gearmember 144 with the transmission housing 160, and the clutch 154connects the sun gear member 122 with the planet carrier assembly member126. The planet carrier assembly members 126 and 146 rotate at the samespeed as the sun gear member 122, the input shaft 17, and the ring gearmembers 124 and 134. The sun gear member 132 rotates at the same speedas the sun gear member 142. The planet carrier assembly member 136rotates at the same speed as the output shaft 19. The speed of theplanet carrier assembly member 136 is determined from the speed of thering gear member 134, the speed of the sun gear member 132, and the ringgear/sun gear tooth ratio of the planetary gear set 130. The ring gearmember 144 does not rotate. The speed of the planet carrier assemblymember 146 is determined from the speed of the sun gear member 142, andthe ring gear/sun gear tooth ratio of the planetary gear set 140. Theoverall numerical value of the fifth forward speed ratio is determinedfrom the tooth ratios of the planetary gear sets 130 and 140.

As set forth above, the truth table of FIG. 2b describes the engagementsequence of the torque transmitting mechanisms utilized to provide areverse drive ratio and five forward speed ratios. It can be readilydetermined from the truth table that all the single step forwardinterchanges are of the single transition type, as are the double stepforward interchanges. The truth table also provides an example of theratios that can be attained with the family members shown in FIG. 2autilizing the sample tooth ratios given in FIG. 2b. The R1/S1 value isthe tooth ratio of the planetary gear set 120; the R2/S2 value is thetooth ratio of the planetary gear set 130; and the R3/S3 value is thetooth ratio of the planetary gear set 140. Also shown in FIG. 2b are theratio steps between single step ratios in the forward direction as wellas the reverse to first ratio step. For example, the first to secondstep ratio is 1.74.

Turning to FIG. 3a, a powertrain 210 includes the engine and torqueconverter 12, a planetary transmission 214, and a final drive mechanism16. The planetary transmission 214 includes an input shaft 17continuously connected with the engine and torque converter 12, aplanetary gear arrangement 218, and an output shaft 19 continuouslyconnected with the final drive mechanism 16. The planetary geararrangement 218 includes three planetary gear sets 220, 230 and 240.

The planetary gear set 220 includes a sun gear member 222, a ring gearmember 224, and a planet carrier assembly 226. The planet carrierassembly 226 includes a plurality of pinion gears 227 rotatably mountedon a carrier member 229 and disposed in meshing relationship with boththe sun gear member 222 and the ring gear member 224.

The planetary gear set 230 includes a sun gear member 232, a ring gearmember 234, and a planet carrier assembly member 236. The planet carrierassembly member 236 includes a plurality of pinion gears 237 rotatablymounted on a carrier member 239 and disposed in meshing relationshipwith both the sun gear member 232 and the ring gear member 234.

The planetary gear set 240 includes a sun gear member 242, a ring gearmember 244, and a planet carrier assembly member 246. The planet carrierassembly member 246 includes a plurality of pinion gears 247 rotatablymounted on a carrier member 249 and disposed in meshing relationshipwith both the sun gear member 242 and the ring gear member 244.

The planetary gear arrangement 218 also includes four torquetransmitting mechanisms 250, 252, 254 and 256. The torque-transmittingmechanisms 250 and 252 are stationary-type torque-transmittingmechanisms, commonly termed brakes or reaction clutches. The torquetransmitting mechanisms 254 and 256 are of the rotating type torquetransmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member222, and the output shaft 19 is continuously connected with the planetcarrier assembly member 236. The sun gear member 222 is continuouslyconnected with the sun gear member 232 through the interconnectingmember 270. The ring gear member 224 is continuously connected with thering gear member 244 through the interconnecting member 272. The ringgear member 234 is continuously connected with the planet carrierassembly member 246 through the interconnecting member 274.

The planet carrier assembly member 226 is selectively connectable withthe transmission housing 260 through the brake 250. The sun gear member242 is selectively connectable with the transmission housing 260 throughthe brake 252. The ring gear member 224 is selectively connectable withthe planet carrier assembly member 236 through the clutch 254. The sungear member 242 is selectively connectable with the planet carrierassembly member 246 through the clutch 256.

As shown in the truth table in FIG. 3b, the torque transmittingmechanisms are engaged in combinations of two to establish five forwardspeed ratios and one reverse ratio. It should be also noted that thetorque transmitting mechanism 250 can remain engaged through the neutralcondition, thereby simplifying the forward/reverse interchange.

To establish the reverse speed ratio, the brake 250 and clutch 254 areengaged. The brake 250 connects the planet carrier assembly member 226with the transmission housing 260, and the clutch 254 connects the ringgear member 224 with the planet carrier assembly member 236. The planetcarrier assembly member 226 does not rotate. The ring gear member 224rotates at the same speed as the ring gear member 244, the planetcarrier assembly member 236, and the output shaft 19. The sun gearmember 222 rotates at the same speed as the input shaft 17 and the sungear member 232. The speed of the ring gear member 224 is determinedfrom the speed of the sun gear member 222 and the ring gear/sun geartooth ratio of the planetary gear set 220. The overall numerical valueof the reverse speed ratio is determined from the tooth ratio of theplanetary gear set 220.

The first forward speed ratio is established with the engagement of thebrake 250 and clutch 256. The brake 250 connects the planet carrierassembly member 226 with the transmission housing 260, and the clutch256 connects the sun gear member 242 with the planet carrier assemblymember 246. The ring gear member 224 rotates at the same speed as thering gear member 244. The sun gear member 222 rotates at the same speedas the input shaft 17 and the sun gear member 232. The planet carrierassembly member 226 does not rotate. The speed of the ring gear member224 is determined from the speed of the sun gear member 222 and the ringgear/sun gear tooth ratio of the planetary gear set 220. The ring gearmembers 234 and 244 rotate at the same speed as the planet carrierassembly member 246 and the sun gear member 242. The planet carrierassembly member 236 rotates at the same speed as the output shaft 19.The planet carrier assembly member 236 rotates at a speed determined bythe speed of the ring gear member 234, the speed of the sun gear member232, and the ring gear/sun gear tooth ratio of the planetary gear set230. The overall numerical value of the first forward speed ratio isdetermined from the tooth ratios of the planetary gear sets 220 and 230.

The second forward speed ratio is established with the engagement of thebrakes 250 and 252. The brake 250 connects the planet carrier assemblymember 226 with the transmission housing 260. The brake 252 connects thesun gear member 242 with the transmission housing 260. The ring gearmember 224 rotates at the same speed as the ring gear member 244. Thesun gear member 222 rotates at the same speed as the input shaft 17 andthe sun gear member 232. The planet carrier assembly member 226 does notrotate. The ring gear member 224 rotates at a speed determined by thespeed of the sun gear member 222 and the ring gear/sun gear tooth ratioof the planetary gear set 220. The ring gear member 234 rotates at thesame speed as the planet carrier assembly member 246. The planet carrierassembly member 236 rotates at the same speed as the output shaft 19,which speed is determined by the speed of the ring gear member 234, thespeed of the sun gear member 232, and the ring gear/sun gear tooth ratioof the planetary gear set 230. The sun gear 242 does not rotate. Thespeed of the planet carrier assembly member 246 is determined from thespeed of the ring gear member 244 and the ring gear/sun gear tooth ratioof the planetary gear set 240. The overall numerical value of the secondforward speed ratio is determined from the tooth ratios of the planetarygear sets 220, 230 and 240.

The third forward speed ratio is established with the engagement of thebrake 252 and the clutch 256. The brake 252 connects the sun gear member242 with the transmission housing 260. The clutch 256 connects the sungear member 242 with the planet carrier assembly member 246.Accordingly, the ring gear members 224, 234, and 244, planet carrierassembly member 246 and sun gear member 242 do not rotate. The sun gearmember 232 rotates at the same speed as the sun gear member 222 and theinput shaft 17. The planet carrier assembly member 236 rotates at thesame speed as the output shaft 19. The planet carrier assembly member236 rotates at a speed determined by the speed of the sun gear member232 and the ring gear/sun gear tooth ratio of the planetary gear set230. The overall numerical value of the third forward speed ratio isdetermined from the tooth ratio of the planetary gear set 230.

The fourth forward speed ratio is established with the engagement of thebrake 252 and the clutch 254. The brake 252 connects the sun gear member242 with the transmission housing 260. The clutch 254 connects the ringgear member 224 with the planet carrier assembly member 236. The ringgear member 234 rotates at the same speed as the planet carrier assemblymember 246. The sun gear member 232 rotates at the same speed as the sungear member 222 and the input shaft 17. The planet carrier assemblymember 236 rotates at the same speed as the output shaft 19, the ringgear member 224, and the ring gear member 244. The speed of the planetcarrier assembly member 236 is determined from the speed of the ringgear member 234, the speed of the sun gear member 232, and the ringgear/sun gear tooth ratio of the planetary gear set 230. The sun gearmember 242 does not rotate. The planet carrier assembly member 246rotates at a speed determined by the speed of the ring gear member 244and the ring gear/sun gear tooth ratio of the planetary gear set 240.The overall numerical value of the fourth forward speed ratio isdetermined from the tooth ratios of the planetary gear sets 230 and 240.

The fifth forward speed ratio is established with the engagement of theclutches 254 and 256. In this configuration, the input shaft 17 isdirectly connected with the output shaft 19. The overall numerical valueof the fifth forward speed ratio is 1.

As previously set forth, the truth table of FIG. 3b describes thecombinations of engagements utilized for the five forward speed ratiosand one reverse ratio. The truth table also provides an example of speedratios that are available with the family member described above. Theseexamples of speed ratios are determined utilizing the tooth ratios givenin FIG. 3b. The R1/S1 value is the tooth ratio of the planetary gear set220; the R2/S2 value is the tooth ratio of the planetary gear set 230;and the R3/S3 value is the tooth ratio of the planetary gear set 240.Also depicted in FIG. 3b is a chart representing the ratio steps betweenadjacent forward speed ratios and the reverse to first forward speedratio. For example, the first to second ratio interchange has a step of1.41. It can also be readily determined from the truth table of FIG. 3bthat all of the single step forward ratio interchanges are of the singletransition variety, as are all of the double step forward interchanges.

A powertrain 310, shown in FIG. 4a, includes the engine and torqueconverter 12, a planetary transmission 314, and the final drivemechanism 16. The planetary transmission 314 includes an input shaft 17continuously connected with the engine and torque converter 12, aplanetary gear arrangement 318, and output shaft 19 continuouslyconnected with the final drive mechanism 16. The planetary geararrangement 318 includes three planetary gear sets 320, 330 and 340.

The planetary gear set 320 includes a sun gear member 322, a ring gearmember 324, and a planet carrier assembly member 326. The planet carrierassembly member 326 includes a plurality of pinion gears 327 rotatablymounted on a carrier member 329 and disposed in meshing relationshipwith both the sun gear member 322 and the ring gear member 324.

The planetary gear set 330 includes a sun gear member 332, a ring gearmember 334, and a planet carrier assembly member 336. The planet carrierassembly member 336 includes a plurality of pinion gears 337 rotatablymounted on a carrier member 339 and disposed in meshing relationshipwith both the sun gear member 332 and the ring gear member 334.

The planetary gear set 340 includes a sun gear member 342, a ring gearmember 344, and a planet carrier assembly member 346. The planet carrierassembly member 346 includes a plurality of pinion gears 347 rotatablymounted on a carrier member 349 and disposed in meshing relationshipwith both the sun gear member 342 and the ring gear member 344.

The planetary gear arrangement 318 also includes four torquetransmitting mechanisms 350, 352, 354 and 356. The torque-transmittingmechanisms 350 and 352 are stationary-type torque-transmittingmechanisms, commonly termed brakes or reaction clutches. The torquetransmitting mechanisms 354 and 356 are of the rotating type torquetransmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member322, and the output shaft 19 is continuously connected with the planetcarrier assembly member 336. The sun gear member 322 is continuouslyconnected with the ring gear member 334 through the interconnectingmember 370. The ring gear member 324 is continuously connected with theplanet carrier assembly member 346 through the interconnecting member372. The sun gear member 332 is continuously connected with the ringgear member 344 through the interconnecting member 374.

The planet carrier assembly member 326 is selectively connectable to thetransmission housing 360 through the brake 350. The sun gear member 342is selectively connectable with the transmission housing 360 through thebrake 352. The planet carrier assembly member 336 is connectable withthe planet carrier assembly member 346 through the clutch 354. The sungear member 342 is selectively connectable with the planet carrierassembly member 346 through the clutch 356.

The truth tables given in FIGS. 4b, 5 b, 6 b, 7 b, 8 b, 9 b, 10 b, 11 b,12 b, 13 b, 14 b, 15 b and 16 b show the engagement sequences for thetorque transmitting mechanisms to provide at least five forward speedratios and one reverse ratio. As shown and described for theconfigurations in FIGS. 1a, 2 a and 3 a, those skilled in the art willunderstand from the respective truth tables how the speed ratios areestablished through the planetary gear sets identified in the writtendescription.

The truth table shown in FIG. 4b describes the engagement combinationand the engagement sequence necessary to provide the reverse drive ratioand the five forward speed ratios. A sample of the numerical values forthe ratios is also provided in the truth table of FIG. 4b. These valuesare determined utilizing the ring gear/sun gear tooth ratios also givenin FIG. 4b. The R1/S1 value is the tooth ratio for the planetary gearset 320; the R2/S2 value is the tooth ratio for the planetary gear set330; and the R3/S3 value is the tooth ratio for the planetary gear set340. Also given in FIG. 4b is a chart describing the step ratios betweenthe adjacent forward speed ratios and the reverse to first forward speedratio. For example, the first to second forward speed ratio step is1.40. It can be readily determined from the truth table of FIG. 4b thateach of the forward single step ratio interchanges is a singletransition shift, as are the double step interchanges. The chart alsoshows that the torque transmitting mechanism 350 can be engaged throughthe neutral condition to simplify the forward/reverse interchange.

Those skilled in the art will recognize that the numerical value of thereverse speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 320. The numerical value of the firstforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 320, 330 and 340. The numerical valueof the second forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 320 and 330. Thenumerical value of the third forward speed ratio is determined utilizingthe ring gear/sun gear tooth ratio of the planetary gear set 330. Thenumerical value of the fourth forward speed ratio is 1. The numericalvalue of the fifth forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 330 and 340.

A powertrain 410, shown in FIG. 5a, includes the engine and torqueconverter 12, a planetary transmission 414 and the final drive mechanism16. The planetary transmission 414 includes a planetary gear arrangement418, input shaft 17 and output shaft 19. The planetary gear arrangement418 includes three simple planetary gear sets 420, 430 and 440.

The planetary gear set 420 includes a sun gear member 422, a ring gearmember 424, and a planet carrier assembly 426. The planet carrierassembly 426 includes a plurality of pinion gears 427 rotatably mountedon a carrier member 429 and disposed in meshing relationship with boththe sun gear member 422 and the ring gear member 424.

The planetary gear set 430 includes a sun gear member 432, a ring gearmember 434, and a planet carrier assembly member 436. The planet carrierassembly member 436 includes a plurality of pinion gears 437 rotatablymounted on a carrier member 439 and disposed in meshing relationshipwith both the sun gear member 432 and the ring gear member 434.

The planetary gear set 440 includes a sun gear member 442, a ring gearmember 444, and a planet carrier assembly member 446. The planet carrierassembly member 446 includes a plurality of pinion gears 447 rotatablymounted on a carrier member 449 and disposed in meshing relationshipwith both the sun gear member 442 and the ring gear member 444.

The planetary gear arrangement 418 also includes four torquetransmitting mechanisms 450, 452, 454 and 456. The torque transmittingmechanisms 450 and 452 are stationary-type torque transmittingmechanisms, commonly termed brakes or reaction clutches. The torquetransmitting mechanisms 454 and 456 are of the rotating type torquetransmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member432, and the output shaft 19 is continuously connected with the planetcarrier assembly member 426. The sun gear member 422 is continuouslyconnected with the sun gear member 432 through the interconnectingmember 470. The ring gear member 424 is continuously connected with theplanet carrier assembly member 446 through the interconnecting member472. The ring gear member 434 is continuously connected with the ringgear member 444 through the interconnecting member 474.

The planet carrier assembly member 436 is selectively connectable withthe transmission housing 460 through the brake 450. The sun gear member442 is selectively connectable with the transmission housing 460 throughthe brake 452. The sun gear member 442 is selectively connectable withthe planet carrier assembly member 446 through the clutch 454. Theplanet carrier assembly member 426 is selectively connectable with thering gear member 434 through the clutch 456.

The truth table shown in FIG. 5b describes the engagement combinationand sequence of the torque transmitting mechanisms 450, 452, 454 and 456that are employed to provide the reverse drive ratio and the fiveforward speed ratios. It should be noted that the torque transmittingmechanism 450 is engaged through the neutral condition to simplify theforward/reverse interchange.

Also given in the truth table of FIG. 5b is a set of numerical valuesthat are attainable with the present invention utilizing the ringgear/sun gear tooth ratios shown. The R1/S1 value is the tooth ratio ofthe planetary gear set 420; the R2/S2 value is the tooth ratio of theplanetary gear set 430; and the R3/S3 value is the tooth ratio of theplanetary gear set 440. As can also be determined from the truth tableof FIG. 5b, the single step forward interchanges are single transitionshifts, as are the double step interchanges in the forward direction.

FIG. 5b also provides a chart of the ratio steps between adjacentforward ratios and between the reverse and first forward ratio. Forexample, the ratio step between the first and second forward ratios is1.44.

Those skilled in the art will recognize that the numerical value of thereverse speed ratio is determined utilizing the tooth ratio of theplanetary gear set 430. The numerical value of the first forward speedratio is determined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 420 and 430. The numerical value of the secondforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 420, 430 and 440. The numerical valueof the third forward speed ratio is determined utilizing the ringgear/sun gear tooth ratio of the planetary gear set 420. The numericalvalue of the fourth forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 420 and 440. Thenumerical value of the fifth forward speed ratio is 1.

A powertrain 510, shown in FIG. 6a, includes an engine and torqueconverter 12, a planetary gear transmission 514 and the final drivemechanism 16. The planetary transmission 514 includes the input shaft17, a planetary gear arrangement 518 and the output shaft 19. Theplanetary gear arrangement 518 includes three planetary gear sets 520,530 and 540.

The planetary gear set 520 includes a sun gear member 522, a ring gearmember 524, and a planet carrier assembly 526. The planet carrierassembly 526 includes a plurality of pinion gears 527 rotatably mountedon a carrier member 529 and disposed in meshing relationship with boththe sun gear member 522 and the ring gear member 524.

The planetary gear set 530 includes a sun gear member 532, a ring gearmember 534, and a planet carrier assembly member 536. The planet carrierassembly member 536 includes a plurality of pinion gears 537 rotatablymounted on a carrier member 539 and disposed in meshing relationshipwith both the sun gear member 532 and the ring gear member 534.

The planetary gear set 540 includes a sun gear member 542, a ring gearmember 544, and a planet carrier assembly member 546. The planet carrierassembly member 546 includes a plurality of pinion gears 547 rotatablymounted on a carrier member 549 and disposed in meshing relationshipwith both the sun gear member 542 and the ring gear member 544.

The planetary gear arrangement 518 also includes four torquetransmitting mechanisms 550, 552, 554 and 556. The torque-transmittingmechanisms 550 and 552 are stationary-type torque-transmittingmechanisms, commonly termed brakes or reaction clutches. The torquetransmitting mechanisms 554 and 556 are of the rotating type torquetransmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member532, and the output shaft 19 is continuously connected with the planetcarrier assembly member 526. The ring gear member 524 is continuouslyconnected with the sun gear member 532 through the interconnectingmember 570. The sun gear member 522 is continuously connected with thering gear member 544 through the interconnecting member 572. The ringgear member 534 is continuously connected with the planet carrierassembly member 546 through the interconnecting member 574.

The planet carrier assembly member 536 is selectively connectable withthe transmission housing 560 through the brake 550. The sun gear member542 is selectively connectable with the transmission housing 560 throughthe brake 552. The planet carrier assembly member 526 is selectivelyconnectable with the ring gear member 534 through the clutch 554. Theplanet carrier assembly member 546 is selectively connectable with thesun gear member 542 through the clutch 556.

The truth table shown in FIG. 6b describes the engagement sequence andcombination of the torque transmitting mechanisms to provide the reversespeed ratio and five forward speed ratios. It should be noted that thetorque transmitting mechanism 550 can remain engaged through the neutralcondition, thereby simplifying the forward/reverse interchange. It canalso be determined from the truth table of FIG. 6b that all of thesingle step forward ratio interchanges are of the single transitionvariety, as are all of the double step forward interchanges. The chartof FIG. 6b describes the ratio steps between adjacent forward speedratios and the ratio step between the reverse and first forward speedratio.

Those skilled in the art, upon reviewing the truth table and theschematic representation of FIG. 6a, can determine that the numericalvalue of the reverse speed ratio is determined utilizing the ringgear/sun gear tooth ratio of the planetary gear set 530. The numericalvalue of the first forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 520, 530 and 540.The numerical value of the second forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets520 and 530. The numerical value of the third forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratio of the planetarygear set 520. The numerical value of the fourth forward speed ratiois 1. The numerical value of the fifth forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets520 and 540.

The sample speed ratios given in the truth table are determinedutilizing the tooth ratio values also given in FIG. 6b. The R1/S1 valueis the tooth ratio of the planetary gear set 520; the R2/S2 value is thetooth ratio of the planetary gear set 530; and the R3/S3 value is thetooth ratio of the planetary gear set 540.

A powertrain 610, shown in FIG. 7a, has the engine and torque converter12, a planetary transmission 614 and the final drive mechanism 16. Theplanetary transmission 614 includes the input shaft 17, a planetary geararrangement 618 and the output shaft 19. The planetary gear arrangement618 includes three planetary gear sets 620, 630 and 640.

The planetary gear set 620 includes a sun gear member 622, a ring gearmember 624, and a planet carrier assembly 626. The planet carrierassembly 626 includes a plurality of pinion gears 627 rotatably mountedon a carrier member 629 and disposed in meshing relationship with boththe sun gear member 622 and the ring gear member 624.

The planetary gear set 630 includes a sun gear member 632, a ring gearmember 634, and a planet carrier assembly member 636. The planet carrierassembly member 636 includes a plurality of pinion gears 637 rotatablymounted on a carrier member 639 and disposed in meshing relationshipwith both the sun gear member 632 and the ring gear member 634.

The planetary gear set 640 includes a sun gear member 642, a ring gearmember 644, and a planet carrier assembly member 646. The planet carrierassembly member 646 includes a plurality of pinion gears 647 rotatablymounted on a carrier member 649 and disposed in meshing relationshipwith both the sun gear member 642 and the ring gear member 644.

The planetary gear arrangement 618 also includes four torquetransmitting mechanisms 650, 652, 654 and 656. The torque-transmittingmechanisms 650 and 652 are stationary-type torque-transmittingmechanisms, commonly termed brakes or reaction clutches. The torquetransmitting mechanisms 654 and 656 are of the rotating type torquetransmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member642, and the output shaft 19 is continuously connected with the ringgear member 624. The sun gear member 622 is continuously connected withthe sun gear member 632 through the interconnecting member 670. Theplanet carrier assembly member 626 is continuously connected with thering gear member 644 through the interconnecting member 672. The ringgear member 634 is continuously connected with the planet carrierassembly member 646 through the interconnecting member 674.

The sun gear member 622 is selectively connectable with the transmissionhousing 660 through the brake 650. The planet carrier assembly member636 is selectively connectable with the transmission housing 660 throughthe brake 652. The ring gear member 624 is selectively connectable withthe planet carrier assembly member 646 through the clutch 654. The sungear member 642 is selectively connectable with the planet carrierassembly member 646 through the clutch 656.

The truth table shown in FIG. 7b describes the combination of torquetransmitting mechanism engagements that will provide the reverse driveratio and the five forward speed ratios, as well as the sequence ofthese engagements and interchanges. The torque transmitting mechanism650 can be engaged through the neutral condition, thereby simplifyingthe forward/reverse interchange. It can be noted from the truth tablethat each of the single step forward interchanges are single transitionratio changes, and the double step forward interchanges are also singletransition ratio changes.

The ratio values given are by way of example and are establishedutilizing the ring gear/sun gear tooth ratios given in FIG. 7b. Forexample, the R1/S1 value is the tooth ratio of the planetary gear set620; the R2/S2 value is the tooth ratio of the planetary gear set 630;and the R3/S3 value is the tooth ratio of the planetary gear set 640.The ratio steps between adjacent forward ratios and the reverse to firstratio are also given in FIG. 7b.

Those skilled in the art will, upon reviewing the truth table of FIG.7b, recognize that the reverse and second forward speed ratios havenumerical values determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 620 and 640. The numerical value ofthe first forward speed ratio is determined utilizing the ring gear/sungear tooth ratios of the planetary gear sets 620, 630 and 640. The thirdforward speed ratio is 1. The numerical value of the fourth forwardspeed ratio is determined utilizing the ring gear/sun gear tooth ratioof the planetary gear set 620. The numerical value of the fifth forwardspeed ratio is determined utilizing the ring gear/sun gear tooth ratiosof the planetary gear sets 620 and 630.

A powertrain 710, shown in FIG. 8a, has the conventional engine andtorque converter 12, a planetary transmission 714, and the conventionalfinal drive mechanism 16. The engine and torque converter 12 aredrivingly connected with the planetary transmission 714 through theinput shaft 17. The planetary transmission 714 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 714 includes a planetary gear arrangement 718that has a first planetary gear set 720, a second planetary gear set730, and a third planetary gear set 740.

The planetary gear set 720 includes a sun gear member 722, a ring gearmember 724, and a planet carrier assembly 726. The planet carrierassembly 726 includes a plurality of pinion gears 727 rotatably mountedon a carrier member 729 and disposed in meshing relationship with boththe sun gear member 722 and the ring gear member 724.

The planetary gear set 730 includes a sun gear member 732, a ring gearmember 734, and a planet carrier assembly member 736. The planet carrierassembly member 736 includes a plurality of pinion gears 737 rotatablymounted on a carrier member 739 and disposed in meshing relationshipwith both the sun gear member 732 and the ring gear member 734.

The planetary gear set 740 includes a sun gear member 742, a ring gearmember 744, and a planet carrier assembly member 746. The planet carrierassembly member 746 includes a plurality of pinion gears 747 rotatablymounted on a carrier member 749 and disposed in meshing relationshipwith both the sun gear member 742 and the ring gear member 744.

The planetary gear arrangement 718 also includes four torquetransmitting mechanisms 750, 752, 754 and 756. The torque transmittingmechanisms 750 and 752 are stationary-type torque transmittingmechanisms, commonly termed brakes or reaction clutches. The torquetransmitting mechanisms 754 and 756 are of the rotating type torquetransmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member732, and the output shaft 19 is continuously connected with the ringgear member 724. The planet carrier assembly member 726 is continuouslyconnected with the ring gear member 734 through the interconnectingmember 770. The sun gear member 722 is continuously connected with thesun gear member 742 through the interconnecting member 772. The planetcarrier assembly member 736 is continuously connected with the ring gearmember 744 through the interconnecting member 774.

The sun gear member 742 is selectively connectable with the transmissionhousing 760 through the brake 750. The planet carrier assembly member746 is selectively connectable with the transmission housing 760 throughthe brake 752. The planet carrier assembly member 726 is selectivelyconnectable with the planet carrier assembly member 736 through theclutch 754. The ring gear member 724 is selectively connectable with theplanet carrier assembly member 736 through the clutch 756.

The truth table of FIG. 8b defines the torque transmitting mechanismengagement sequence utilized for each of the forward speed ratios andthe reverse speed ratio. Also given in the truth table is a set ofnumerical values that are attainable with the present inventionutilizing the ring gear/sun gear tooth ratios given in FIG. 8b. TheR1/S1 value is the tooth ratio of the planetary gear set 720; the R2/S2value is the tooth ratio of the planetary gear set 730; and the R3/S3value is the tooth ratio of the planetary gear set 740. As can also bedetermined from the truth table of FIG. 8b, the single step forwardinterchanges are single transition shifts, as are the double stepinterchanges in the forward direction.

FIG. 8b also provides a chart of the ratio steps between adjacentforward ratios and between the reverse and first forward ratio. Forexample, the ratio step between the first and second forward ratios is1.71. Those skilled in the art will recognize that the numerical valuesof the reverse and second forward speed ratios are determined utilizingthe ring gear/sun gear tooth ratios of the planetary gear sets 720 and730. The numerical value of the first forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets720, 730 and 740. The numerical value of the third forward speed ratiois 1. The numerical value of the fourth forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratio of the planetarygear set 720. The numerical value of the fifth forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 720 and 740.

A powertrain 810, shown in FIG. 9a, has the conventional engine andtorque converter 12, a planetary transmission 814, and the final drivemechanism 16. The engine and torque converter 12 are drivingly connectedwith the planetary transmission 814 through the input shaft 17. Theplanetary transmission 814 is drivingly connected with the final drivemechanism 16 through the output shaft 19. The planetary transmission 814includes a planetary gear arrangement 818 that has a first planetarygear set 820, a second planetary gear set 830, and a third planetarygear set 840.

The planetary gear set 820 includes a sun gear member 822, a ring gearmember 824, and a planet carrier assembly 826. The planet carrierassembly 826 includes a plurality of pinion gears 827 rotatably mountedon a carrier member 829 and disposed in meshing relationship with boththe sun gear member 822 and the ring gear member 824.

The planetary gear set 830 includes a sun gear member 832, a ring gearmember 834, and a planet carrier assembly member 836. The planet carrierassembly member 836 includes a plurality of pinion gears 837 rotatablymounted on a carrier member 839 and disposed in meshing relationshipwith both the sun gear member 832 and the ring gear member 834.

The planetary gear set 840 includes a sun gear member 842, a ring gearmember 844, and a planet carrier assembly member 846. The planet carrierassembly member 846 includes a plurality of pinion gears 847 rotatablymounted on a carrier member 849 and disposed in meshing relationshipwith both the sun gear member 842 and the ring gear member 844.

The planetary gear arrangement 818 also includes four torquetransmitting mechanisms 850, 852, 854 and 856. The torque-transmittingmechanisms 850 and 852 are stationary-type torque-transmittingmechanisms, commonly termed brakes or reaction clutches. The torquetransmitting mechanisms 854 and 856 are of the rotating type torquetransmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member822, and the output shaft 19 is continuously connected with the planetcarrier assembly member 836. The ring gear member 824 is continuouslyconnected with the planet carrier assembly member 836 through theinterconnecting member 870. The planet carrier assembly member 826 iscontinuously connected with the planet carrier assembly member 846through the interconnecting member 872. The sun gear member 832 iscontinuously connected with the ring gear member 844 through theinterconnecting member 874.

The ring gear member 844 is selectively connectable with thetransmission housing 860 through the brake 850. The sun gear member 842is selectively connectable with the transmission housing 860 through thebrake 852. The planet carrier assembly member 826 is selectivelyconnectable with the ring gear member 834 through the clutch 854. Thesun gear member 822 is selectively connectable with the ring gear member834 through the clutch 856.

The truth table shown in FIG. 9b defines the torque transmittingmechanism engagement sequence that provides the reverse ratio and fiveforward speed ratios shown in the truth table and available with theplanetary gear arrangement 818. The truth table indicates that thetorque transmitting mechanism 850 can remain engaged through the neutralcondition, thereby simplifying the forward/reverse interchange. A sampleof numerical values for the individual ratios is also given in the truthtable of FIG. 9b. These numerical values have been calculated utilizingthe ring gear/sun gear tooth ratios also given by way of example in FIG.9b. The R1/S1 value is the tooth ratio of the planetary gear set 820;the R2/S2 value is the tooth ratio of the planetary gear set 830; andthe R3/S3 value is the tooth ratio of the planetary gear set 840. It canbe readily recognized from the truth table that all of the single anddouble step forward interchanges are single transition ratiointerchanges. FIG. 9b also describes the ratio steps between adjacentforward ratios and between the reverse and first forward ratio. Forexample, the ratio step between the first and second forward ratios is1.74.

Those skilled in the art of planetary transmissions will recognize thatthe numerical value of the reverse speed ratio is determined utilizingthe ring gear/sun gear tooth ratio of the planetary gear set 820. Thenumerical value of the first and second forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 820 and 830. The numerical value of the thirdforward speed ratio is one. The numerical values of the fourth and fifthforward speed ratios are determined utilizing the ring gear/sun geartooth ratios of the planetary gear sets 820, 830 and 840.

The powertrain 910, shown in FIG. 10a, includes the conventional engineand torque converter 12, a planetary transmission 914, and theconventional final drive mechanism 16. The engine and torque converter12 are drivingly connected with the planetary transmission 914 throughthe input shaft 17. The planetary transmission 914 is drivinglyconnected with the final drive mechanism 16 through the output shaft 19.The planetary transmission 914 includes a planetary gear arrangement 918that has a first planetary gear set 920, a second planetary gear set930, and a third planetary gear set 940.

The planetary gear set 920 includes a sun gear member 922, a ring gearmember 924, and a planet carrier assembly 926. The planet carrierassembly 926 includes a plurality of intermeshing pinion gears 927 thatare rotatably mounted on a carrier member 929 and disposed in meshingrelationship with the sun gear member 922 and the ring gear member 924,respectively.

The planetary gear set 930 includes a sun gear member 932, a ring gearmember 934, and a planet carrier assembly member 936. The planet carrierassembly member 936 includes a plurality of pinion gears 937 rotatablymounted on a carrier member 939 and disposed in meshing relationshipwith both the sun gear member 932 and the ring gear member 934.

The planetary gear set 940 includes a sun gear member 942, a ring gearmember 944, and a planet carrier assembly member 946. The planet carrierassembly member 946 includes a plurality of pinion gears 947 rotatablymounted on a carrier member 949 and disposed in meshing relationshipwith both the sun gear member 942 and the ring gear member 944.

The planetary gear arrangement 918 also includes four torquetransmitting mechanisms 950, 952, 954 and 956. The torque transmittingmechanisms 950 and 952 are stationary-type torque transmittingmechanisms, commonly termed brakes or reaction clutches. The torquetransmitting mechanisms 954 and 956 are of the rotating type torquetransmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member932, and the output shaft 19 is continuously connected with the planetcarrier assembly member 946. The planet carrier assembly member 926 iscontinuously connected with the ring gear member 934 through theinterconnecting member 970. The sun gear member 922 is continuouslyconnected with the sun gear member 942 through the interconnectingmember 972. The planet carrier assembly member 936 is continuouslyconnected with the ring gear member 944 through the interconnectingmember 974.

The sun gear member 922 is selectively connectable with the transmissionhousing 960 through the brake 950. The ring gear member 924 isselectively connectable with the transmission housing 960 through thebrake 952. The ring gear member 924 is selectively connectable with theplanet carrier assembly member 936 through the clutch 954. The planetcarrier assembly member 936 is selectively connectable with the sun gearmember 932 through the clutch 956.

The truth table of FIG. 10b describes the torque transmitting mechanismengagement sequence utilized to provide the reverse speed ratio and fiveforward speed ratios. The truth table also provides a set of examplesfor the ratios for each of the reverse and forward speed ratios. Thesenumerical values have been determined utilizing the ring gear/sun geartooth ratios given in FIG. 10b. The R1/S1 value is the tooth ratio ofthe planetary gear set 920; the R2/S2 value is the tooth ratio of theplanetary gear set 930; and the R3/S3 value is the tooth ratio of theplanetary gear set 940. It can also be determined from the truth tableof FIG. 10b that each of the forward single step and double step ratiointerchanges are of the single transition variety.

Those skilled in the art, upon reviewing the engagement combinations,will recognize that the values of the reverse and second forward speedratios are determined utilizing the ring gear/sun gear tooth ratios ofthe planetary gear sets 920, 930 and 940. The numerical value of thefirst forward speed ratio is determined utilizing the ring gear/sun geartooth ratios of the planetary gear sets 930 and 940. The numerical valueof the third forward speed ratio is determined utilizing the ringgear/sun gear tooth ratio of the planetary gear set 940. The numericalvalue of the fourth forward speed ratio is 1. The numerical value of thefifth forward speed ratio is determined utilizing the ring gear/sun geartooth ratios of the planetary gear sets 920 and 940.

A powertrain 1010, shown in FIG. 11a, includes the conventional engineand torque converter 12, a planetary transmission 1014, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1014 through theinput shaft 17. The planetary transmission 1014 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1014 includes a planetary gear arrangement 1018that has a first planetary gear set 1020, a second planetary gear set1030, and a third planetary gear set 1040.

The planetary gear set 1020 includes a sun gear member 1022, a ring gearmember 1024, and a planet carrier assembly 1026. The planet carrierassembly 1026 includes a plurality of pinion gears 1027 rotatablymounted on a carrier member 1029 and disposed in meshing relationshipwith both the sun gear member 1022 and the ring gear member 1024.

The planetary gear set 1030 includes a sun gear member 1032, a ring gearmember 1034, and a planet carrier assembly member 1036. The planetcarrier assembly member 1036 includes a plurality of pinion gears 1037rotatably mounted on a carrier member 1039 and disposed in meshingrelationship with both the sun gear member 1032 and the ring gear member1034.

The planetary gear set 1040 includes a sun gear member 1042, a ring gearmember 1044, and a planet carrier assembly member 1046. The planetcarrier assembly member 1046 includes a plurality of pinion gears 1047rotatably mounted on a carrier member 1049 and disposed in meshingrelationship with both the sun gear member 1042 and the ring gear member1044.

The planetary gear arrangement 1018 also includes four torquetransmitting mechanisms 1050, 1052, 1054 and 1056. Thetorque-transmitting mechanisms 1050 and 1052 are stationary-typetorque-transmitting mechanisms, commonly termed brakes or reactionclutches. The torque transmitting mechanisms 1054 and 1056 are of therotating type torque transmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member1022, and the output shaft 19 is continuously connected with the planetcarrier assembly member 1036. The sun gear member 1022 is continuouslyconnected with the sun gear member 1032 through the interconnectingmember 1070. The ring gear member 1024 is continuously connected withthe planet carrier assembly member 1046 through the interconnectingmember 1072. The ring gear member 1034 is continuously connected withthe ring gear member 1044 through the interconnecting member 1074.

The planet carrier assembly member 1046 is selectively connectable withthe transmission housing 1060 through the brake 1050. The sun gearmember 1042 is selectively connectable with the transmission housing1060 through the brake 1052. The planet carrier assembly member 1026 isselectively connectable with the ring gear member 1034 through theclutch 1054. The sun gear member 1042 is selectively connectable withthe planet carrier assembly member 1026 through the clutch 1056.

The truth table shown in FIG. 11b describes the engagement combinationsand the engagement sequence necessary to provide the reverse drive ratioand the five forward speed ratios. A sample of the numerical values forthe ratios is also provided in the truth table of FIG. 11b. These valuesare determined utilizing the ring gear/sun gear tooth ratios also givenin FIG. 11b. The R1/S1 value is the tooth ratio for the planetary gearset 1020; the R2/S2 value is the tooth ratio for the planetary gear set1030; and the R3/S3 value is the tooth ratio for the planetary gear set1040. Also given in FIG. 11b is a chart describing the step ratiosbetween the adjacent forward speed ratios and the reverse to firstforward speed ratio.

Those skilled in the art will recognize that the numerical values of thereverse, first and fourth forward speed ratios are determined utilizingthe ring gear/sun gear tooth ratios of the planetary gear sets 1020,1030 and 1040. The numerical value of the second forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratio of the planetarygear set 1030. The numerical value of the third forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 1020 and 1030. The numerical value of the fifthforward speed ratio is 1.

A powertrain 1110, shown in FIG. 12a, includes the conventional engineand torque converter 12, a planetary transmission 1114, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1114 through theinput shaft 17. The planetary transmission 1114 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1114 includes a planetary gear arrangement 1118that has a first planetary gear set 1120, a second planetary gear set1130, and a third planetary gear set 1140.

The planetary gear set 1120 includes a sun gear member 1122, a ring gearmember 1124, and a planet carrier assembly 1126. The planet carrierassembly 1126 includes a plurality of pinion gears 1127 rotatablymounted on a carrier member 1129 and disposed in meshing relationshipwith both the sun gear member 1122 and the ring gear member 1124.

The planetary gear set 1130 includes a sun gear member 1132, a ring gearmember 1134, and a planet carrier assembly member 1136. The planetcarrier assembly member 1136 includes a plurality of pinion gears 1137rotatably mounted on a carrier member 1139 and disposed in meshingrelationship with both the sun gear member 1132 and the ring gear member1134.

The planetary gear set 1140 includes a sun gear member 1142, a ring gearmember 1144, and a planet carrier assembly member 1146. The planetcarrier assembly member 1146 includes a plurality of pinion gears 1147rotatably mounted on a carrier member 1149 and disposed in meshingrelationship with both the sun gear member 1142 and the ring gear member1144.

The planetary gear arrangement 1118 also includes four torquetransmitting mechanisms 1150, 1152, 1154 and 1156. The torquetransmitting mechanisms 1150 and 1152 are stationary-type torquetransmitting mechanisms, commonly termed brakes or reaction clutches.The torque transmitting mechanisms 1154 and 1156 are of the rotatingtype torque transmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member1142, and the output shaft 19 is continuously connected with the ringgear member 1144. The ring gear member 1124 is continuously connectedwith the planet carrier assembly member 1136 through the interconnectingmember 1170. The planet carrier assembly member 1126 is continuouslyconnected with the ring gear member 1144 through the interconnectingmember 1172. The ring gear member 1134 is continuously connected withthe planet carrier assembly member 1146 through the interconnectingmember 1174.

The sun gear member 1122 is selectively connectable with thetransmission housing 1160 through the brake 1150. The sun gear member1132 is selectively connectable with the transmission housing 1160through the brake 1152. The planet carrier assembly member 1136 isselectively connectable with the sun gear member 1132 through the clutch1154. The planet carrier assembly member 1136 is selectively connectablewith the sun gear member 1142 through the clutch 1156.

The truth table shown in FIG. 12b describes the engagement combinationsand the engagement sequence necessary to provide the reverse drive ratioand the five forward speed ratios. A sample of the numerical values forthe ratios is also provided in the truth table of FIG. 12b. These valuesare determined utilizing the ring gear/sun gear tooth ratios also givenin FIG. 12b. The R1/S1 value is the tooth ratio for the planetary gearset 1120; the R2/S2 value is the tooth ratio for the planetary gear set1130; and the R3/S3 value is the tooth ratio for the planetary gear set1140. Also given in FIG. 12b is a chart describing the step ratiosbetween the adjacent forward speed ratios and the reverse to firstforward speed ratio.

Those skilled in the art will recognize that the numerical value of thereverse speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 1140. The numerical value of the firstforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 1120, 1130 and 1140. The numericalvalue of the second forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 1120 and 1140. Thenumerical value of the third forward speed ratio is determined utilizingthe ring gear/sun gear tooth ratio of the planetary gear set 1120. Thenumerical value of the fourth forward speed ratio is 1. The numericalvalue of the fifth forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 1130 and 1140.

A powertrain 1210, shown in FIG. 13a, includes the conventional engineand torque converter 12, a planetary transmission 1214, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1214 through theinput shaft 17. The planetary transmission 1214 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1214 includes a planetary gear arrangement 1218that has a first planetary gear set 1220, a second planetary gear set1230, and a third planetary gear set 1240.

The planetary gear set 1220 includes a sun gear member 1222, a ring gearmember 1224, and a planet carrier assembly 1226. The planet carrierassembly 1226 includes a plurality of pinion gears 1227 rotatablymounted on a carrier member 1229 and disposed in meshing relationshipwith both the sun gear member 1222 and the ring gear member 1224.

The planetary gear set 1230 includes a sun gear member 1232, a ring gearmember 1234, and a planet carrier assembly member 1236. The planetcarrier assembly member 1236 includes a plurality of pinion gears 1237and 1238 rotatably mounted on a carrier member 1239 and disposed inmeshing relationship with both the sun gear member 1232 and the ringgear member 1234.

The planetary gear set 1240 includes a sun gear member 1242, a ring gearmember 1244, and a planet carrier assembly member 1246. The planetcarrier assembly member 1246 includes a plurality of pinion gears 1247rotatably mounted on a carrier member 1249 and disposed in meshingrelationship with both the sun gear member 1242 and the ring gear member1244.

The planetary gear arrangement 1218 also includes four torquetransmitting mechanisms 1250, 152, 1254 and 1256. The torquetransmitting mechanisms 1250 and 1252 are stationary-type torquetransmitting mechanisms, commonly termed brakes or reaction clutches.The torque transmitting mechanisms 1254 and 1256 are of the rotatingtype torque transmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member1232, and the output shaft 19 is continuously connected with the planetcarrier assembly member 1246. The ring gear member 1224 is continuouslyconnected with the ring gear member 1234 through the interconnectingmember 1270. The planet carrier assembly member 1226 is continuouslyconnected with the ring gear member 1244 through the interconnectingmember 1272. The planet carrier assembly member 1236 is continuouslyconnected with the planet carrier assembly member 1246 through theinterconnecting member 1274.

The sun gear member 1222 is selectively connectable with thetransmission housing 1260 through the brake 1250. The sun gear member1242 is selectively connectable with the transmission housing 1260through the brake 1252. The sun gear member 1222 is selectivelyconnectable with the planet carrier assembly member 1226 through theclutch 1254. The planet carrier assembly member 1226 is selectivelyconnectable with the sun gear member 1232 through the clutch 1256.

The truth table shown in FIG. 13b describes the engagement combinationsand the engagement sequence necessary to provide the reverse drive ratioand the five forward speed ratios. A sample of the numerical values forthe ratios is also provided in the truth table of FIG. 13b. These valuesare determined utilizing the ring gear/sun gear tooth ratios also givenin FIG. 13b. The R1/S1 value is the tooth ratio for the planetary gearset 1220; the R2/S2 value is the tooth ratio for the planetary gear set1230; and the R3/S3 value is the tooth ratio for the planetary gear set1240. Also given in FIG. 13b is a chart describing the step ratiosbetween the adjacent forward speed ratios and the reverse to firstforward speed ratio.

Those skilled in the art will recognize that the numerical value of thereverse speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 1230. The numerical value of the firstforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 1220, 1230 and 1240. The numericalvalue of the second forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 1230 and 1240. Thenumerical value of the third forward speed ratio is determined utilizingthe ring gear/sun gear tooth ratio of the planetary gear set 1240. Thenumerical value of the fourth forward speed ratio is 1. The numericalvalue of the fifth forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 1220 and 1230.

A powertrain 1310, shown in FIG. 14a, includes the conventional engineand torque converter 12, a planetary transmission 1314, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1314 through theinput shaft 17. The planetary transmission 1314 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1314 includes a planetary gear arrangement 1318that has a first planetary gear set 1320, a second planetary gear set1330, and a third planetary gear set 1340.

The planetary gear set 1320 includes a sun gear member 1322, a ring gearmember 1324, and a planet carrier assembly 1326. The planet carrierassembly 1326 includes a plurality of pinion gears 1327 and 1328rotatably mounted on a carrier member 1329 and disposed in meshingrelationship with both the sun gear member 1322 and the ring gear member1324.

The planetary gear set 1330 includes a sun gear member 1332, a ring gearmember 1334, and a planet carrier assembly member 1336. The planetcarrier assembly member 1336 includes a plurality of pinion gears 1337rotatably mounted on a carrier member 1339 and disposed in meshingrelationship with both the sun gear member 1332 and the ring gear member1334.

The planetary gear set 1340 includes a sun gear member 1342, a ring gearmember 1344, and a planet carrier assembly member 1346. The planetcarrier assembly member 1346 includes a plurality of pinion gears 1347rotatably mounted on a carrier member 1349 and disposed in meshingrelationship with both the sun gear member 1342 and the ring gear member1344.

The planetary gear arrangement 1318 also includes four torquetransmitting mechanisms 1350, 1352, 1354 and 1356. The torquetransmitting mechanisms 1350 and 1352 are stationary-type torquetransmitting mechanisms, commonly termed brakes or reaction clutches.The torque transmitting mechanisms 1354 and 1356 are of therotating-type torque transmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member1322. The output shaft 19 is continuously connected with the planetcarrier assembly member 1336. The sun gear member 1322 is continuouslyconnected with the ring gear member 1334 through the interconnectingmember 1370. The planet carrier assembly member 1326 is continuouslyconnected with the planet carrier assembly member 1346 through theinterconnecting member 1372. The sun gear member 1332 is continuouslyconnected with the ring gear member 1344 through the interconnectingmember 1374.

The ring gear member 1324 is selectively connectable with thetransmission housing 1360 through the brake 1350. The sun gear member1342 is selectively connectable with the transmission housing 1360through the brake 1352. The planet carrier assembly member 1326 isselectively connectable with the planet carrier assembly member 1336through the clutch 1354. The sun gear member 1332 is selectivelyconnectable with the sun gear member 1342 through the clutch 1356.

The truth table shown in FIG. 14b describes the engagement combinationsand the engagement sequence necessary to provide the reverse drive ratioand the five forward speed ratios. A sample of the numerical values forthe ratios is also provided in the truth table of FIG. 14b. These valuesare determined utilizing the ring gear/sun gear tooth ratios also givenin FIG. 14b. The R1/S1 value is the tooth ratio for the planetary gearset 1320; the R2/S2 value is the tooth ratio for the planetary gear set1330; and the R3/S3 value is the tooth ratio for the planetary gear set1340. Also given in FIG. 14b is a chart describing the step ratiosbetween the adjacent forward speed ratios and the reverse to firstforward speed ratio.

Those skilled in the art will recognize that the numerical value of thereverse speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 1320. The numerical value of the firstforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 1320, 1330 and 1340. The numericalvalue of the second forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gears 1320 and 1330. Thenumerical value of the third forward speed ratio is determined utilizingthe ring gear/sun gear tooth ratio of the planetary gear set 1330. Thenumerical value of the fourth forward speed ratio is 1. The numericalvalue of the fifth forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 1330 and 1340.

A powertrain 1410, shown in FIG. 15a, includes the conventional engineand torque converter 12, a planetary transmission 1414, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1414 through theinput shaft 17. The planetary transmission 1414 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1414 includes a planetary gear arrangement 1418that has a first planetary gear set 1420, a second planetary gear set1430, and a third planetary gear set 1440.

The planetary gear set 1420 includes a sun gear member 1422, a ring gearmember 1424, and a planet carrier assembly 1426. The planet carrierassembly 1426 includes a plurality of pinion gears 1427 rotatablymounted on a carrier member 1429 and disposed in meshing relationshipwith both the sun gear member 1422 and the ring gear member 1424.

The planetary gear set 1430 includes a sun gear member 1432, a ring gearmember 1434, and a planet carrier assembly member 1436. The planetcarrier assembly member 1436 includes a plurality of pinion gears 1437rotatably mounted on a carrier member 1439 and disposed in meshingrelationship with both the sun gear member 1432 and the ring gear member1434.

The planetary gear set 1440 includes a sun gear member 1442, a ring gearmember 1444, and a planet carrier assembly member 1446. The planetcarrier assembly member 1446 includes a plurality of pinion gears 1447rotatably mounted on a carrier member 1449 and disposed in meshingrelationship with both the sun gear member 1442 and the ring gear member1444.

The planetary gear arrangement 1418 also includes four torquetransmitting mechanisms 1450, 1452, 1454 and 1456. The torquetransmitting mechanisms 1450 and 1452 are a stationary-type torquetransmitting mechanisms, commonly termed brakes or reaction clutches.The torque transmitting mechanisms 1454 and 1456 are of the rotatingtype torque transmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the sun gear member1422, and the output shaft 19 is continuously connected with the planetcarrier assembly member 1446. The ring gear member 1424 is continuouslyconnected with the planet carrier assembly member 1436 through theinterconnecting member 1470. The planet carrier assembly member 1426 iscontinuously connected with the ring gear member 1444 through theinterconnecting member 1472. The ring gear member 1434 is continuouslyconnected with the planet carrier assembly member 1446 through theinterconnecting member 1474.

The sun gear member 1432 is selectively connectable with thetransmission housing 1460 through the brake 1450. The sun gear member1442 is selectively connectable with the transmission housing 1460through the brake 1452. The planet carrier assembly member 1426 isselectively connectable with the sun gear member 1422 through the clutch1454. The planet carrier assembly member 1426 is selectively connectablewith the sun gear member 1432 through the clutch 1456.

The truth table shown in FIG. 15b describes the engagement combinationsand the engagement sequence necessary to provide the reverse drive ratioand the five forward speed ratios. A sample of the numerical values forthe ratios is also provided in the truth table of FIG. 15b. These valuesare determined utilizing the ring gear/sun gear tooth ratios also givenin FIG. 15b. The R1/S1 value is the tooth ratio for the planetary gearset 1420; the R2/S2 value is the tooth ratio for the planetary gear set1430; and the R3/S3 value is the tooth ratio for the planetary gear set1440. Also given in FIG. 15b is a chart describing the step ratiosbetween the adjacent forward speed ratios and the reverse to firstforward speed ratio.

Those skilled in the art will recognize that the numerical value of thereverse speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 1420 and 1430. The numerical values ofthe first and second forward speed ratios are determined utilizing thering gear/sun gear tooth ratios of the planetary gear sets 1420, 1430and 1440. The numerical value of the third forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratio of the planetarygear set 1440. The numerical value of the fourth forward speed ratiois 1. The numerical value of the fifth forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratio of the planetary gear set1430.

A powertrain 1510, shown in FIG. 16a, includes the conventional engineand torque converter 12, a planetary transmission 1514, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1514 through theinput shaft 17. The planetary transmission 1514 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1514 includes a planetary gear arrangement 1518that has a first planetary gear set 1520, a second planetary gear set1530, and a third planetary gear set 1540.

The planetary gear set 1520 includes a sun gear member 1522, a ring gearmember 1524, and a planet carrier assembly 1526. The planet carrierassembly 1526 includes a plurality of pinion gears 1527 rotatablymounted on a carrier member 1529 and disposed in meshing relationshipwith both the sun gear member 1522 and the ring gear member 1524.

The planetary gear set 1530 includes a sun gear member 1532, a ring gearmember 1534, and a planet carrier assembly member 1536. The planetcarrier assembly member 1536 includes a plurality of pinion gears 1537rotatably mounted on a carrier member 1539 and disposed in meshingrelationship with both the sun gear member 1532 and the ring gear member1534.

The planetary gear set 1540 includes a sun gear member 1542, a ring gearmember 1544, and a planet carrier assembly member 1546. The planetcarrier assembly member 1546 includes a plurality of pinion gears 1547rotatably mounted on a carrier member 1549 and disposed in meshingrelationship with both the sun gear member 1542 and the ring gear member1544.

The planetary gear arrangement 1518 also includes four torquetransmitting mechanisms 1550, 1552, 1554 and 1556. The torquetransmitting mechanism 1550 and 1552 are stationary-type torquetransmitting mechanisms, commonly termed brakes or reaction clutches.The torque transmitting mechanism 1554 and 1556 are of the rotating-typetorque transmitting mechanisms, commonly termed clutches.

The input shaft 17 is continuously connected with the ring gear member1534, and the output shaft 19 is continuously connected with the ringgear member 1544. The sun gear member 1522 is continuously connectedwith the sun gear member 1532 through the interconnecting member 1570.The planet carrier assembly member 1526 is continuously connected withthe sun gear member 1542 through the interconnecting member 1572. Theplanet carrier assembly member 1536 is continuously connected with thering gear member 1544 through the interconnecting member 1574.

The ring gear member 1524 is selectively connectable with thetransmission housing 1560 through the brake 1550. The planet carrierassembly member 1546 is selectively connectable with the transmissionhousing 1560 through the brake 1552. The planet carrier assembly member1526 is selectively connectable with the sun gear member 1532 throughthe clutch 1554. The planet carrier assembly member 1526 is selectivelyconnectable with the ring gear member 1534 through the clutch 1556.

The truth table shown in FIG. 16b describes the engagement combinationsand the engagement sequence necessary to provide the reverse drive ratioand the five forward speed ratios. A sample of the numerical values forthe ratios is also provided in the truth table of FIG. 16b. These valuesare determined utilizing the ring gear/sun gear tooth ratios also givenin FIG. 16b. The R1/S1 value is the tooth ratio for the planetary gearset 1520; the R2/S2 value is the tooth ratio for the planetary gear set1530; and the R3/S3 value is the tooth ratio for the planetary gear set1540. Also given in FIG. 16b is a chart describing the step ratiosbetween the adjacent forward speed ratios and the reverse to firstforward speed ratio.

Those skilled in the art will recognize that the numerical value of thereverse speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 1540. The numerical value of the firstforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 1520, 1530 and 1540. The numericalvalue of the second forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 1530 and 1540. Thenumerical value of the third forward speed ratio is determined utilizingthe ring gear/sun gear tooth ratio of the planetary gear set 1530. Thenumerical value of the fourth forward speed ratio is 1. The numericalvalue of the fifth forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 1520 and 1530.

While the best modes for carrying out the invention have been describedin detail, those familiar with the art to which this invention relateswill recognize various alternative designs and embodiments forpracticing the invention within the scope of the appended claims.

What is claimed is:
 1. A multi-speed transmission comprising: an inputshaft; an output shaft; a planetary gear arrangement having not morethan first, second and third planetary gear sets1 each planetary gearset having first, second and third members; said input shaft beingcontinuously interconnected with a member of the planetary gear sets,said output shaft being continuously interconnected with another memberof the planetary gear sets; a first interconnecting member continuouslyinterconnecting said first member of said first planetary gear set withsaid first member of said second planetary gear set; a secondinterconnecting member continuously interconnecting said second memberof said first planetary gear set with said first member of said thirdplanetary gear set; a third interconnecting member continuouslyinterconnecting said second member of said second planetary gear setwith said second member of said third planetary gear set; a first brakeselectively interconnecting a transmission housing with a member of saidfirst or second planetary gear set, said member interconnected with saidfirst brake being different from the members continuously interconnectedwith said input shaft or output shaft; a second brake selectivelyinterconnecting said transmission housing with a member of said secondor third planetary gear set, said member interconnected with said secondbrake being different from the members continuously interconnected withsaid input shaft or output shaft; a first clutch selectivelyinterconnecting a member of said first planetary gear set with anothermember of said planetary gear sets; a second clutch selectivelyinterconnecting a member of said third planetary gear set with anothermember of said planetary gear sets; and said first and second brakes andsaid first and second clutches being engaged in combinations of two toestablish at least five forward speed ratios and a reverse speed ratiobetween said input shaft and said output shaft.
 2. The transmissiondefined in claim 1, wherein planet carrier assembly members of each ofsaid planetary gear set are of the single-pinion type.
 3. Thetransmission defined in claim 1, wherein planet carrier assembly membersof at least one of said planetary gear sets is of the double-piniontype.
 4. A multi-speed transmission comprising: an input shaft; anoutput shaft; a planetary gear arrangement having not more than first,second and third planetary gear sets, each planetary gear set havingfirst, second and third members; said input shaft being continuouslyinterconnected with a member of the planetary gear sets, said outputshaft being continuously interconnected with another member of theplanetary gear sets; a first interconnecting member continuouslyinterconnecting said first member of said first planetary gear set withsaid first member of said second planetary gear set; a secondinterconnecting member continuously interconnecting said second memberof said first planetary gear set with said first member of said thirdplanetary gear set; a third interconnecting member continuouslyinterconnecting said second member of said second planetary gear setwith said second member of said third planetary gear set; and twoselectively engageable brakes and two selectively engageable clutchesfor selectively interconnecting said members of said planetary gear setsand a transmission housing in combinations of two to establish at leastfive forward speed ratios and one reverse speed ratio between said inputshaft and said output shaft.
 5. The transmission defined in claim 4,wherein a first of said two brakes is selectively operable forinterconnecting said transmission housing with a member of said first orsecond planetary gear set1 said member interconnected with said firstbrake being different from the members continuously interconnected withsaid input shaft or output shaft.
 6. The transmission defined in claim4, wherein a second of said two brakes is selectively operable forinterconnecting said transmission housing with a member of said secondor third planetary gear sets said member interconnected with said secondbrake being different from the members continuously interconnected withsaid input shaft or output shaft.
 7. The transmission defined in claim4, wherein a first of said two clutches is selectively operable forinterconnecting a member of said first planetary gear set with anothermember of said planetary gear sets.
 8. The transmission defined in claim4, wherein a second of said two clutches is selectively operable forinterconnecting a member of said third planetary gear set with anothermember of said planetary gear sets.
 9. The transmission defined in claim4, wherein planet carrier assembly members of each of said planetarygear sets are of the single-pinion type.
 10. The transmission defined inclaim 4, wherein a planet carrier assembly member of at least one ofsaid planetary gear sets is of the double-pinion type.
 11. A multi-speedtransmission comprising: an input shaft; an output shaft; a planetarygear arrangement having not more than first, second and third planetarygear sets, each planetary gear set having first, second and thirdmembers; said input shaft being continuously interconnected with amember of the planetary gear sets, said output shaft being continuouslyinterconnected with another member of the planetary gear sets; a firstinterconnecting member continuously interconnecting said first member ofsaid first planetary gear set with said first member of said secondplanetary gear set; a second interconnecting member continuouslyinterconnecting said second member of said first planetary gear set withsaid first member of said third planetary gear set; a thirdinterconnecting member continuously interconnecting said second memberof said second planetary gear set with said second member of said thirdplanetary gear set; first and second brakes and first and secondclutches being selectively engageable to establish combinations ofmembers joined for common rotation to provide five forward speed ratiosand one reverse speed ratio between said input shaft and said outputshaft, said combinations including either: an engaged combination withsaid first brake selectively interconnecting said third member of saidsecond planetary gear set with said transmission housing, said secondbrake selectively interconnecting said third member of said thirdplanetary gear set with said transmission housing, said first clutchselectively interconnecting said third member of said first planetarygear set with said second member of said third planetary gear set, andsaid second clutch selectively interconnecting said third member of saidthird planetary gear set with said second member of said third planetarygear set; or an engaged combination with said first brake selectivelyinterconnecting said second member of said second planetary gear setwith said transmission housing, said second brake selectivelyinterconnecting said third member of said third planetary gear set withsaid transmission housing, said first clutch selectively interconnectingsaid first member of said first planetary gear set with said thirdmember of said first planetary gear set, and said second clutchselectively interconnecting said first member of said first planetarygear set with said third member of said third planetary gear set; or anengaged combination with said first brake selectively interconnectingsaid third member of said first planetary gear set with saidtransmission housing, said second brake selectively interconnecting saidthird member of said third planetary gear set with said transmissionhousing, said first clutch selectively interconnecting said secondmember of said first planetary gear set with said third member of saidsecond planetary gear set, and said second clutch selectivelyinterconnecting said second member of said third planetary gear set withsaid third member of said third planetary gear set; or an engagedcombination with said first brake selectively interconnecting said thirdmember of said first planetary gear set with said transmission housing,said second brake selectively interconnecting said third member of saidthird planetary gear set with said transmission housing, said firstclutch selectively interconnecting said second member of said firstplanetary gear set with said third member of said third planetary gearset, and said second clutch selectively interconnecting said thirdmember of said second planetary gear set with said first member of saidthird planetary gear set; or an engaged combination with said firstbrake selectively interconnecting said third member of said secondplanetary gear set with said transmission housing, said second brakeselectively interconnecting said third member of said third planetarygear set with said transmission housing, said first clutch selectivelyinterconnecting said third member of said first planetary gear set withsaid second member of said second planetary gear set, and said secondclutch selectively interconnecting said first member of said thirdplanetary gear set with said third member of said third planetary gearset; or an engaged combination with said first brake selectivelyinterconnecting said third member of said second planetary gear set withsaid transmission housing, said second brake selectively interconnectingsaid third member of said third planetary gear set with saidtransmission housing, said first clutch selectively interconnecting saidthird member of said first planetary gear set with said second member ofsaid second planetary gear set, and said second clutch selectivelyinterconnecting said second member of said third planetary gear set withsaid third member of said third planetary gear set; or an engagedcombination with said first brake selectively interconnecting said firstmember of said first planetary gear set with said transmission housing,said second brake selectively interconnecting said third member of saidsecond planetary gear set with said transmission housing, said firstclutch selectively interconnecting said third member of said firstplanetary gear set with said second member of said third planetary gearset, and said second clutch selectively interconnecting said secondmember of said third planetary gear set with said third member of saidthird planetary gear set; or an engaged combination with said firstbrake selectively interconnecting said second member of said firstplanetary gear set with said transmission housing, said second brakeselectively interconnecting said third member of said third planetarygear set with said transmission housing, said first clutch selectivelyinterconnecting said third member of said first planetary gear set withsaid second member of said second planetary gear set, and said secondclutch selectively interconnecting said first member of said secondplanetary gear set with said second member of said third planetary gearset; or an engaged combination with said first brake selectivelyinterconnecting said second member of said second planetary gear setwith said transmission housing, said second brake selectivelyinterconnecting said third member of said third planetary gear set withsaid transmission housing, said first clutch selectively interconnectingsaid third member of said first planetary gear set with said thirdmember of said third planetary gear set, and said second clutchselectively interconnecting said second member of said first planetarygear set with said third member of said third planetary gear set; or anengaged combination with said first brake selectively interconnectingsaid third member of said first planetary gear set with saidtransmission housing, said second brake selectively interconnecting saidfirst member of said third planetary gear set with said transmissionhousing, said first clutch selectively interconnecting said third memberof said first planetary gear set with said second member of said secondplanetary gear set, and said second clutch selectively interconnectingsaid second member of said second planetary gear set with said thirdmember of said second planetary gear set; or an engaged combination withsaid first brake selectively interconnecting said second member of saidfirst planetary gear set with said transmission housing, said secondbrake selectively interconnecting said third member of said thirdplanetary gear set with said transmission housing, said first clutchselectively interconnecting said third member of said first planetarygear set with said second member of said second planetary gear set, andsaid second clutch selectively interconnecting said third member of saidfirst planetary gear set with said third member of said third planetarygear set; or an engaged combination with said first brake selectivelyinterconnecting said third member of said first planetary gear set withsaid transmission housing, said second brake selectively interconnectingsaid third member of said second planetary gear set with saidtransmission housing, said first clutch selectively interconnecting saidfirst member of said first planetary gear set with said third member ofsaid second planetary gear set, and second clutch selectivelyinterconnecting said first member of said second planetary gear set withsaid third member of said third planetary gear set; or an engagedcombination with said first brake selectively interconnecting said thirdmember of said first planetary gear set with said transmission housing,said second brake selectively interconnecting said third member of saidthird planetary gear set with said transmission housing, said firstclutch selectively interconnecting said second member of said firstplanetary gear set with said third member of said second planetary gearset, and said second clutch selectively interconnecting said firstmember of said third planetary gear set with said third member of saidfirst planetary gear set; or an engaged combination with said firstbrake selectively interconnecting said third member of said firstplanetary gear set with said transmission housing, said second brakeselectively interconnecting said third member of said third planetarygear set with said transmission housing, said first clutch selectivelyinterconnecting said third member of said second planetary gear set withsaid second member of said first planetary gear set, and said secondclutch selectively interconnecting said second member of said secondplanetary gear set with said third member of said third planetary gearset; or an engaged combination with said first brake selectivelyinterconnecting said third member of said second planetary gear set withsaid transmission housing, said second brake selectively interconnectingsaid third member of said third planetary gear set with saidtransmission housing, said first clutch selectively interconnecting saidsecond member of said first planetary gear set with said third member ofsaid second planetary gear set, and said second clutch selectivelyinterconnecting said first member of said third planetary gear set withsaid third member of said first planetary gear set; or an engagedcombination with said first brake selectively interconnecting said thirdmember of said first planetary gear set with said transmission housing,said second brake selectively interconnecting said third member of saidthird planetary gear set with said transmission housing, said firstclutch selectively interconnecting said second member of said firstplanetary gear set with said third member of said second planetary gearset, and said second clutch selectively interconnecting said firstmember of said third planetary gear set with said first member of saidfirst planetary gear set.